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H11 u T e M w a e N l H a M i I l l a n m 0 m a a Q l 9 4. n m 1 I "II i 0 n INVENTORS Jose 4k J &fiwmarm BY 7710mm; Mtarler IWTOIYNEY Patented Sept. 5, 1950 WEB TENSION CONTROL MEANS Joseph S. Scheuermann and Thomas N. Carter, Chicago, 111., assignors to Cameron Machine Company, Brooklyn, N. Y., a corporation of New York Application November 16, 1944, Serial No. 563,780 1 Claim. (Cl. 242-19 This invention relates to machines employing a tensioned running web of flexible material, such as paper or the like, in which machines a carriage, capable of a back-and-forth movement, supports a tension-control roll that engages a bight or loop in the running web.

In such machines it has been customary to employ a power device, consisting of a flexible connection passing over a sheave and carrying weights at its free end, as a means for exerting a constant pull on the carriage, to thereby force the tension-control roll with a constant pressure into engagement with the bight in the web.

Such weights are cumbersome and heavy to handle when it is desired to change from one constant pressure of the tension-control roll against the web to another constant pressure of said roll. Moreover, if the web should suddenly become greatly slackened or break, the consequent sudden descent of the weights could be quite disastrous to the attendants at the machine as well as to the machine itself.

The main object and feature of this invention is to provide a power device, for the carriage that supports the tension-control roll, operated and controlled by fluid-pressure, preferably air pressure, whereby the objectionable weights can be dispensed with.

In the accompanying drawings, the invention is disclosed in several concrete and preferred forms, in which:

Fig. 1 is a somewhat diagrammatic view in side elevation showing one form of the invention applied to two types of machines, one, an unwinding mechanism for a web of flexible material and, another, a winding machine for said web;

Fig. 2 is a horizontal sectional detail view substantially on the plane of line 2--2 of Fig. 1;

Fig. 3 is a vertical sectional view substantially on the plane of line 3-3 of Fig. 1;

Fig. 4 is a vertical sectional detail view substantially on the plane of line 4-4 of Fig. 3;

Figs. 5, 6 and 7 are vertical sectional views through a valve-mechanism that may be used in connection with the invention. Fig. 5 shows the position of the parts when they are in equilibrium; Fig. 6 shows the position of the parts when the inlet valve is open and the outlet valve is closed; and Fig. 7 shows the position of the parts when the outlet valve is open and the inlet valve is closed;

Fig. 8 is a view similar to Fig. 1 but showing a modified form of the invention;

Fig. 9 is a horizontal sectional view substantially on the plane of irregular line 9--9 of Fig. 8, showing parts of the unwinding mechanism;

Fig. 10 is a horizontal sectional view substantially on the plane of irregular line l9--l9' of Fig. 8, showing parts of the winding machine;

Fig. 11 is a sectional view of one type of fluidactuated operating device such as may be used either in connection with the brake rod of the brake of the unwinding mechanism of Figs. 8 and 9, or with the clutch rod of the slip-friction drive of the winding machine of Figs. 8 and 10;

Fig. 12 is a vertical sectional view through a valve-mechanism and means for actuating same to be used in connection with the forms of the invention shown in Figs. 8 to 11 inclusive;

Fig. 13 is a fragmentary plan view of Fig. 14 showing still another form of the invention; and

Fig. 14 is a view partly in side elevation and partly in section of the parts shown in Fig. 13.

It will facilitate an explanation and understanding of the broad aspects of the invention and of the fluid-pressure power device if attention is first directed to Fig. 4. As there shown, the web under tension is indicated at W, and 29 denotes a tension-control roll rotatably mounted on carriage or shaft 26 and engaging the bight or loop in said web. Carriage 26 is capable of a back-and-forth movement in guide 21 in a, wellunderstood manner. 28 is a fluid-pressure receiver connected by means of a duct 29 to a source of supply of fluid-pressure (not shown). Receiver 23 is provided with an expansible and contractible fluid-pressure receiving chamber such as would be afforded by a cylinder and piston or byv a chamber having a flexible diaphragm. In the construction shown, the chamber, indicated by 39, is formed between two flexible diaphragms. 3| and 32, for reasons that will presently appear,

so that the chamber takes on the character of bellows. 33 indicates valve-mechanism, interposed in duct 29, and it will be suflicient for immediate purposes to state that the function of said valve-mechanism is to maintain the same predetermined fluid-pressure within chamber 39, notwithstanding the expansion or contraction of said chamber; the details of construction of said valve-mechanism 33 will be described later. Suitable power-transmission and connecting means, here generally indicated by the reference character 34, responsive to fluid-pressure in chamber 39 and to the tension of the web against roll 25, are provided, also to be presently described.

From the foregoing it will now be understood that, when a slack develops in the bight of web W, carriage 26 and thereby roll 25 will move to the right (in Fig. 4) under compulsion of fluidpressure in chamber 39. This will expand chamber 39 and will therefore tend to diminish fluidpressure within said chamber, the immediate effect of which will be to cause valve-mechanism 33 to supply .fiuid-pressure to chamber 39 to thereby maintain the same predetermined pressure, as previously existed, of roll 25 against the web. When valve-mechanism 33 has established the predetermined fluid-pressure in chamber 39. it will automatically shut itself on. Conversely,

when the tension of web W becomes excessive, roll 28 and thereby carriage 28 will move to the left (in Fig. 4), thereby contracting chamber 88. This will therefore tend to increase the fluidpressure within chamber 88, the immediate effect of which will be to cause valve-mechanism 88 to exhaust fluid-pressure from chamber 88, to thereby maintain the same predetermined pressure, as previously existed, of roll 25 against the web. When valve-mechanism 88 has established the predetermined fluid-pressure in chamber 88, it will automatically close the exhaust.

A general understanding of the construction and operation of the invention having now been obtained, a more detailed description will be given.

Referring again to Fig. 4 and receiver 28, means are provided to translate simultaneous opposite movements of diaphragms 8| and 82 into a unidirectional movement of power-transmission and connecting means 84 which, in the present instance, take the following form: 85 and 88 indicate two axially alined shafts, to slidably sustain receiver 28, extending into said receiver from opposite sides thereof. One shaft 85 is connected to the central portion of diaphragm 8| by means of clamping discs 81, and the other shaft 88 is connected to central portion of diaphragm 82 by means of clamping discs 88. Shaft 85' is pivotally supported extraneously of receiver 28 and held against endwise movement by support 88, whereas shaft 88 is connected by connecting means, here consisting of threaded extension 48, to power-transmission member 4|, which latter is movably mounted extraneously of receiver 28. Receiver 28 here consists of three members, one central member 42 and two outer members 48, held together by means of bolts'44. Diaphragms 8| and 82 are clamped at their peripheries between members '42 and 48 as shown. Receiver 28 is further provided with sleeve extensions 45 surrounding shafts 85 and 88. 48 is a shut-off valve to close communication from duct 28 to chamber 88, and 41 is a drain valve from said chamber 88. Forming part of power-transmission means 84, is a rocker-lever 48 pivotally supported at 48 to rocker-bar 58, which latter is pivotally carried on pivot 5| of framework 52. Lever 48 is connected to carriage or shaft 28 as by bushing 58 loosely surrounding said shaft so as to follow, or impart, the back-and-forth movement of shaft 28 without following its rotation, and power-transmission member 4| is connected to lever 48 by pivotal connection 54.

From the foregoing, it wfll now be seen that the expansion of chamber 88 produced by the simultaneous movement of diaphragms 8| and 82 in opposite directions will cause not only shaft 88 to move to the right (in Fig. 4) but will also produce a sliding movement of receiver 28 and its sleeves 45 to the right (in Fig. 4). By these means the movement of lever 48 (and thereby of carriage 28 and roll 25) will have twice the amplitude that would be produced if but a single diaphragm were used. Conversely, movement of lever 48 to the left (in Fig. 4), when web tension becomes excessive, will cause return to the left (in Fig. 4) of both shaft 88 and receiver 28. Furthermore, as it is desired, in this instance, that the back-and-forth movement of shaft or carriage 28 shall be a straight-line movement, it will be seen that lever 48 which rocks on pivot 48, will move bar 58 up and down by turning it on pivotal center 5|. It will also be observed that pivotal connection 54 allows rocking movement of lever 48 while permitting a straight-line movement of shaft 88 and receiver 28.

From the foregoing, it will also be seen that rocker-bar 58 constitutes a floating support for rocker-lever 48, and that shafts 85 and 88 (which are parallel to rocker-bar 58) together with receiver 28 constitute floating means that are pivotally connected to rocker-lever 48 at an in termediate point thereof. To allow rocking or floating movement of receiver 28, part of duct 28 will be flexible as shown.

Attention is now directed to Figs. 5, 6 and 7 for a full explanation of valve-mechanism 88.

The casing of valve-mechanism 88 is divided into a high-pressure chamber 55, connected to the source of supply of fluid-pressure (not shown), and a low-pressure chamber 58 connected to receiver 28. 51 is an inlet valve to open or close port 58 between the high and low-pres sure chambers, said inlet valve being urged into its closed position by spring 58. 88 is an outlet valve to open or close port or exhaust 8|. Valves 81 and 88 are connected by means of a valve stem 82 so as to move in unison. 88 is a movable valve seat, having port 8|, associated with said outlet valve 88. 84 and 85 are two controllers, for said valve-mechanism, acting in opposition to each other. One of these, 84, exerts a constant pressure to which it has been adjusted. The other, 85, is a flexible diaphragm, the edges of which are anchored in the casing as shown, which engages movable valve seat 88 within low-pressure chamber 58 of the valvemechanism and is thus responsive to fluid-pressure in receiver 28. Controller 84 consists here of a. stem 88 in threaded engagement with, and adiustable in, guide 81 and bearing against spring seat 88, between which latter and movable valve seat 88, a spring 88 is interposed. Stem 88 is provided with a handle I8 by means of which its position can be adjusted to thereby vary the pressure or tension of spring 88 in opposition to the force exerted by controller 85. Thus the operation of valve-mechanism 88 is controlled by twofactors: the predetermined pressure exerted by controller 84, and the fluid-pressure is chamber 88 of receiver 28 acting through controller diaphragm 85. This action will now be described in detail.

When the fluid-pressure in receiver 28 is such as to press control roll 25 into engagement with the web to create therein the desired tension, the force exerted by spring 88 of controller 84 against valve seat 88, and the fluid-pressure exerted against diaphragm controller 85 plus the force of spring 58 on inlet valve 51 will be equalized. The parts of the valve-mechanism will therefore be in the position shown in Fig. 5, and inlet valve 51 and outlet valve 88 will both be in closed position. When chamber 88 of receiver 28 expands, owing to the formation of slack in the web, the fluid-pressure therein tends to diminish. Consequently, the force exerted by controller diaphragm 85 diminishes and is overcome by the force exerted by controller 84. This will cause valve seat 88 to"be moved (Fig. 6), carrying with it both outlet valve 88 and inlet valve 51. It will be observed, however, that outlet valve 88 remains in its closed position, although inlet valve 51 is moved to its open position. Fluid under pressure will therefore flow from high-pressure chamber 55 to low-pressure chamber 58 and thence to receiver 28 until the desired predetermined pressure is restored in chamber 88 of recel er 28 when equilibrium is obtained and the 5 parts reassume the position shown in Fig. 5. n the other hand, when the tension of the web becomes excessive against control roll 25, chamber 88 of receiver 28 will contract and the fluidpressure in chamber 38 will tend to increase. This excessive pressure will be exerted against diaphragm controller 65 and will in turn overcome the action of spring 68 of controller 84. This will move valve seat 63.away from outlet valve 80 and port or exhaust 6| will be open while inlet port 58 will remain closed (Fig. 7). The result is that fluid-pressure from receiver 28 will be drained back into low-pressure chamber 58 and out through exhaust 8| until pressure has been reduced in chamber 38 of receiver 28 to the predetermined one, thereby enabling spring 88 of controller 84 to close exhaust 8| by moving valve seat 88 against outlet valve 88, whereupon the parts will reassume the position shown in Fig. 5. g

It will be understood that the avoidance of time-lag is an important consideration in correcting variations in tension of the web. It has been found that provision can be made in the valve-mechanism to give it what might be called a hair-trigger action. This is accomplished (Fig. by providing a small leak H from high-pressure chamber 55 to low-pressure chamber 58, the effect of which is to constantly tend to activate the valve-mechanism without substantially affecting the pressure in chamber 30 of receiver 28. Good results have been obtained with a leak having a diameter of .00175 of an inch. It is, of course, not intended to limit the leak to this particular size, as different machines or operating conditions might require different treatment. To provide for this, there is shown in Fig. 6 an adjustable needle valve 12 controlling leak 1|. In some cases, a similar result can be obtained by providing a leak 13 (Fig. '7) from low-pressure chamber 58 to atmosphere, and this leak likewise can be controlled by an adjustable needle valve I4.

Attention is now directed to Figs. 1, 2 and 3, as well as to Figs. 4 to '1. Referring particularly to Fig. 1, A indicates an unwinding mechanism such as a mill roll stand, and B is a winding machine. 0 is a processing machine such as a printing press which acts on' web W in its passage from A to B. It will be understood that it is not necessary to have a battery of machines such as A, B and C in order to practice the invention; the arrangement shown is merely a convenient way of exemplifying that the invention can be embodied in different machines.

Considering first the construction shown in connection with winding machine B, web W passes over guide rollers I5 and I8 between which is interposed tension-control roll 25 to engage the bight in the web. After leaving guide roller 18, the web passes to winding shaft 11 of the winding machine. As previously indicated, tension-control roll 25 is rotatably supported on a carriage, here consisting of shaft 28, capable of a backand-forth movement in guide 21 (Fig. 2). Adjacent said guide 21 is a stationary rack 18 with which meshes a pinion 18 fast on shaft or carriage 28. The arrangement is in duplicate, there being a guide 21, a rack 18 and a pinion 19 associated with each end of shaft or carriage 28. There is also a receiver 28 and a train of connections, as 84, at each side of the machine and, for this purpose, duct 28 extends to both receivers 28 as shown in Fig. 3, but only one valve-mechanism- 88 is needed to control both receivers 28.

Winding machine B is of the center-wind type, i. e. winding shaft 11 is driven by power applied centrally of said shaft. As the wound material. WM, accumulates on said winding shaft, it will be understood that a greater and greater length of material is taken up with each revolution of said shaft; hence, it is necessary to decrease the speed of said shaft as the winding operation proceeds. Also, the power necessary to drive said winding shaft will, at the beginning of the winding operation, be slight but, as the load on said shaft increases, due to the accumulation of wound material thereon, more and more power is required to drive the shaft if the right web tension is to be maintained. It is therefore customary to employ means to drive winding shaft consisting in part of a variable speed mechanism such as a slip-friction drive or clutch 88 that at first engages lightly and without any, or very little, slippage but which, as the load increases, engages more strongly and has greater slippage.

It has been pointed out that carriage 28 is capable of a back-and-forth'movement but, in the winding machine here under consideration, it is also necessary to have a progressive movement or a movement of traverse of said carriage 28 from near one end of guide 21 to a point adjacent the other end of said guide in order to actuate a clutch-control rod, such as 8|, to increase the action of clutch as the winding operation proceeds. The action of carriage 28 is therefore a gradual movement of traverse from one end of guide 21 to the other, interrupted by slight back-and-forth movements to compensate for temporary variations in tension of the web.

It will further be understood that, in response to the movement of traverse of carriage 28, chamber 88 of receiver 28 will be gradually expanded and that, notwithstanding such expansion, the same fluid-pressure will be maintained within said chamber 88. The means for actuating clutch-control rod 8| from carriage 26 here consist of link 82 connected at one end to lever 48 and at its other end to lever 88. pivoted at 84 on framework 52, said clutch-control rod- 8| being pivotally connected to lever 88.

' Turning now to unwinding mechanism A, it will be understood that a condition there prevails which is the reverse of that in winding machine 13, for there, at the beginning of the unwinding operation, mill roll MR is at its greatest diameter and must therefore be rotated slowly at first, the speed of the mill roll increasing as its diameter diminishes in order to supply the same length of web in a given time. It is customary to provide the mill roll with a variable-speed mechanism, here a variable brake 85, controlled by a brakerod 88. Web W, as it unwinds, passes over guide rolls 81 and 88 between which is interposed tension-control roll 25a mounted on carriage 28a capable of a back-and-forth movement in guide 21a and connected to receiver 28a by means of connections 34a. A duct 28a leads from a source of supply of fluid-pressure (not shown) to receiver 28a and interposed in said duct is valvemechanism 83a. All these parts are constructed brake is applied most strongl at the beginning of carriage 26a from one end to the other of a guide 21a. The progressive traverse oi. said carriage 26a, will nonetheless be interrupted by slight back-and-iorth movements to compensate for temporary variations in tension of the web. However, valve-mechanism 33a will maintain a constant fluid-pressure in chamber 30 of receiver 28a during the gradual contraction of said chamber 30 as well as during temporary expansion or contraction thereof.

In Figs. 1, 2 and 3, the connecting means between carriage 26 or 28a and slip-friction clutch 80 or brake 85 are shown as being wholly mechanical connections. Such means can take other forms.

Attention is now directed to Figs. 8 to 12 inclusive, in which fluid-pressure connections, to a large extent, take the place of the mechanical connections.

In Fig. 8 is shown a view of a battery of machines similar to Fig. 1. AI indicates an unwinding mechanism, BI a winding machine and CI an intermediate processing machine. So far as the elements included in the power device associated with the tension control are concerned, they are, in Figs. 8 to 12 inclusive, the same as those described in connection with Figs. l'to 7 inclusive, and are indicated by the same reference characters but with an added or a different exponent. Thus, in winding machine BI, receiver 280, valve-mechanism 33c, duct 29c, carriage c, tension-control roll 250 etc. are the same as the corresponding elements of 28, 33, 29, 2G, etc. of winding machine B. So, likewise, in unwinding mechanism AI', receiver 28d, valvemechanism 33d, duct 29d, carriage 26d, tensioncontrol roll 25d etc. are the same as the COITG-w sponding elements in unwinding mechanism A. It will therefore be unnecessary to repeat a description of the construction and operation oi. these parts of the machine.

90, or 9| (Fig. 11), indicates a fluid-actuated operating device, which can be of any suitable construction, but which is here in the form of a casin 92 divided by a flexible diaphragm 93. Connected to said casing at one side of the diaphragm is a duct 94 or 95 leading from a source of supply of fluid-pressure (not shown). Connected to said diaphragm is a slidable member 96 pivotally connected to a pivoted lever 91 that engages, in the case of machine AI, a brake-control rod 98 or, in the case of machine BI, a clutch-'- control rod 99.

Interposed in duct 94 or 95, is a valve-mechanism I00 or I 0|, which valve-mechanism (Fig;

12) is here constructed asfollows: The valve casing is divided into a high-pressure chamber I02, connected to the source of supply, and a lowpressure chamber I03, connected to fluid-actuated operating device 90 or 9|, as the case may be. I04 is an inlet valve to open or close port I05 between the high and low-pressure chambers, said inlet valve being urged into its closed positionby spring I06. I0! is an outlet valve to open or close port or exhaust I08. Valves I04 and I0! are connected by means of a valve stem I09 so as to move in unison. I I0 is a movable valve seat, having port I08, associated with said outlet valve I01. I II and III! are two controllers, for said valve-mechanism, acting in opposition to each other. One of these, III', moves in response to movements of carriage 2041 or 28c. The other, H2, is a flexible diaphragm, the edges of which are anchored in the casing as shown, which engages movable valve seat IIO within low-pressure chamber I03 of the valve-mechanism and is thus responsive to fluid-pressure in fluid-actuated operating device 90 or 9|, as the case may be. Controller III' consists here of a plunger 3 movable in guide H4 and bearing against spring seat I I5, between which latter and movable valve seat H0, 8. spring H6 is interposed. The means for operating controller I from reciprocatory carriage 26d or 230. as the case may be, consists of a cam lever II! or III pivoted at 9 or I20 on the framework. The free end of cam lever II'Ior II'0 rests with its cam face on tensioncontrol roll 25d or 200 or other member of carriage 2011 or 23c, so that movements of said carriage will lift or lower the cam lever. Plunger N3 of controller III engages the upper surface of the cam lever and it will be apparent that said plunger will be moved up or down in conformity with the movements of said cam lever, whereby the tension of spring II6 will be varied.

When the fluid-pressure in fluid-actuated operating device 90 or Si is such as to operate the variable speed-control device (brake 05d or clutch 800) to give the required constant web tension in any position of carriage 26d or 26c, the force exerted by spring IIS of controller III against valve seat H0, and the fluid-pressure exerted against diaphragm controller I I2 plus the force of spring I06 on inlet valve I04 will be equalized. The parts of the valve-mechanism will therefore be in a position where inlet valve I04 and outlet valve I01 will both be closed. If the force exerted by the fluid-pressure in fluid-actuated operating device 90 or 9| is insufficient to properly actuate brake d or clutch 000 to maintain the constant tension on the web, then the movement of carriage 20d or 260 will, through the connections described, actuate plunger II 3 of controller II I to increase tension of spring 0 to overcome the force exerted by diaphragm controller 2 and spring I06. This will cause valve seat II 0 to be lifted, carrying with it both outlet valve I01 and inlet valve I04.. It will be observed, however, that outlet valve I01 remains in its closed .position, although inlet valve I04 is moved to its open position. Fluid under pressure will therefore flow from high-pressure chamber I02 -to low-pressure chamber I03 and thence to fluidactuated operating device or 9| until equilibrium is restored and the parts reassume the position shown in Fi 12. On the other hand, if the fluid-pressure in fluid-actuated operating device 90 or 9| is in excess of that required to properly actuate brake 85d or clutch 80c to maintain the constant tension on the web, then the fluid-pressure acting on diaphragm controller I I2 will overcome the action of spring III; and will move valve seat IIO away from outlet valve I01 and port or exhaust I00 will be: open while inlet port I05 remains closed. The result is that fluidpressure from fluid-actuated operating device 90 or 9| will drain back into low-pressure chamber I03 and out through exhaust I00 until pressure has been reduced to enable spring IIG to close port I08 by moving valve seat 0 against outlet valve I01, whereupon the parts will reassume the position shown in Fig. 12. y

In addition tothe foregoing, it must again be 7' borne in mind that, at the beginning of the. un-

9 winding operation of unwinding mechanism AI, brake aid will exert its greatest force, and that, at the beginning of the winding operation of winding machine BI, slip-friction clutch 80c will engage with the least force.

To keep valve I or IOI activated, in the same manner as that described in connection with valve-mechanism 33, a leak I'2I may be provided, from high-pressure chamber I02 to low-pressure chamber I03, and an adjustable valve I22 to control the size of the leak; Or, in certain cases, a leak I23 from low-pressure chamber I03 to atmosphere can be used, and the size of this leak can likewise be regulated by a valve I24.

Valve-mechanism such as 33 (Figs. 5, 6 and '7) and valve such as I00 (Fig. 12) are constructed alike, except that, in case of 33, controller 64 is adjusted to maintain a uniform fluid-pressure in chamber 30 of receiver 28, whereas, in the case of valve I00, the corresponding controller III is used to vary the fluid-pressure in fluid-actuated device 30 in accordance with the movement of the carriage that supports the tensioncontrol roll.

The use of a valve such as I00 and associated elements to actuate variable speed-control devices, such as a variable brake or a variable clutch, disclosed in Figs. 8 to 12 inclusive hereof, forms the subject matter of another application filed June 15, 1944, Ser. No. 540,444, now Patent No.

2,462,558 issued February 22, 1949.

Attention is now directed to Figs. 13 and 14 which show the invention applied to a surfacewinding machine. is one in which the winding of the-material is accomplished by means of a winding shaft resting in the valley between two drums. Such machines are well known and it is unnecessary to describe them in detail. Sufllce it to say that I25 and I26 indicate two winding drums, and I21 indicates the winding shaft on which wound ma terial I28 is accumulated, and as the material accumulates said winding shaft rises in suitable guides I23 in a well-understood manner. Winding drum I25 is driven by pulley I30, and is provided with a gear I3I that meshes with an intermediate gear I32, which latter in turn drives gear I33. of winding drum I26. Thusthe two winding drums, I25 and I26, rotate in the same direction and drive the winding shaft by frictional engagement with the surface of the material being wound. It will be apparent that the winding drums will be driven at a constant'speed, except to compensate for minor variations in tension of the running web so that, if the web slackens, the speed of the winding drums will be slightly increased and, if the tension in the running web becomes excessive, the speed of the winding drums will be slightly decreased.

after which it travels around winding drum I25 to winding shaft I21. Intermediate the guide rollers, I33 and I30, is interposed a tension-control roll 25c mounted on a shaft or carriage c,

which latter is capable of a back-and-forth movement In guide 21:. Tension-control roll 2 en- A surface-winding machine 1o gages a bight or loop in the running web agains which it is presseddgy a group of devices similar inconstruction to those described in connection with the other forms of the invention. ,That is to say: 28s is a receiver constructed and mounted parts readily identify themselves.

In this instance, however, it will be observed" that there is no traverse of carriage 26efrom one end of guide 21s to the other during the windin operation, because no slip-friction clutch is employed, the clutching power of which latter would have to be progressively increased, and because the speed of winding drums I25 and I26 remains constant, except to be varied slightly to take up slack or relieve tension. Consequently, the parts are so adjusted that, when the web is at the right tension, chamber 30c will be approximately halfway expanded, and variations from such central position will compensate for undesired slack or undue tension. So, also, carriage 26c will, under proper tension conditions, occupy substantially a mid-position in guide 21c, and will reciprocate back and forth from that position to keep it in proper engagement with the bight in the web.

Any suitable means, either fluid-pressure or mechanical, can be utilized to transmit the backand-forth movement of carriage 26s to beltshifter I36. ,In the present instance, a bell-crank I40 is pivotally supported at I on the framework, one end of said bell-crank-being connected to carriage 26c by link I42, and the other end of said bell-crank having a slot I43 engaging a pin I44 on belt-shifter fork I36, which latter slides on stationary guide 5.

We claim:

In a machine employing a tensioned running web of flexible material, which machine has tension-control means including a reciprocatory carriage that moves in a straight guide and is provided with a roll that engages abight in said running web, the combination with said carriage; of a rocker-lever pivotally mounted at one end and pivotally connected at the other end to said ca!- riage a rocker-bar pivotally supporting said firstmentioned end of said rocker-lever; and a power device including: two axially alined shafts parallel to said rocker-bar, a pivotal support for one of said shafts, pivotal connecting means between said other shaft and said rocker-leverat an intermediate point of the latter, and means mounted on said shafts to effect lengthwise movement of said other shaft.

JOSEPH S. SCHEUERMANN.

THOMAS N. CARTER.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,i00,039 Tyler et a1 June 16, 1914 1,860,962 Smith May 31, 1932 1,887,578 Bush Nov. 15, 1932 1,936,802 Kai-g N0v.28, 1033 2,252,152 Work Aug. 12, 1041 2,320,101 Mott May 35, 1043 2,331,766 Carter Oct. 12, 1043 

